Flexible vane turbine pump

ABSTRACT

A turbine pump comprising an internally cylindrical case having an annular pump chamber therein, an inlet and outlet in the case communicating with the pump chamber, a rotor drive shaft extending axially into the case, an impeller on the drive shaft incorporating flow vanes made of an elastomeric material.

Elnite Ehsary Sttes 1 May 22, 1973 [73] Assig [21] Appl.

Inventor:

Filed:

FLEXIBLE VANE TU INE PUMP Vivan Richard Ebsary, Palm Beach,

New South Wales, Australia Rockwell Manufacturing Company,

Pittsburgh, Pa.

Nov. 6, 1970 US. Cl. ..4l5/14l, 415/148, 415/213 T Int. Cl ..F0ld 17/12, F03b 3/12, F04d 15/00 Field of Search 418/127-129, 153-156;

415/53 T, 140,141, 146,148,199 T, 213 T References Cited UNITED STATES PATENTS Baker ..4l5/213 T Worst La Bour..... Ferguson ..415/53 T Primary ExaminerWilliam L. Freeh Assistant Examiner-John J. Vrablik Attorney-Emory L. Groff and Emory L. Groff, Jr.

[57] ABSTRACT A turbine pump comprising an internally cylindrical case having an annular pump chamber therein, an inlet and outlet in the case communicating with the pump chamber, a rotor drive shaft extending axially into the case, an impeller on the drive shaft incorporating flow vanes made of an elastomeric material.

5 Claims, 7 Drawing Figures PATENTEDRAYZZIHYS SHEET 1 BF 3 MEL/ff V w/w X. E3 509 FLEXIBLE VANE TURBINE PUMP Flexible vane pumps as constructed hitherto are generally not as efficient as they should be theoretically, the principal reasons being:

1. High starting torque when dry.

2. Permanent deformation of the rotor impeller vane when standing idle for lengthy periods.

3. Constant rotor impeller vane flexing when pump is operating inducing premature fatigue.

4. Damage to rotor impeller vane when operated dry beyond a minimal time.

The present invention has been devised to produce a flexible vane regenerative turbine pump which:

a. is self priming when provided with a head of liquid.

b. incorporates means which can be actuated to prime in a dry start without creating a high starting torque c. when pumping does not subject the rotor impeller vane to excessive contact flexing and promotes long life without fatigue failure.

d. can operate at higher speeds cavitation free e. can pass solids in suspension within the impeller cell structure.

f. incorporate means to expel displaced air or vapors during priming and will eject entrained air or gas when pumping.

Embodiments of the invention are described with reference to the annexed schematic drawings wherein:

FIG. 1 is a longitudinal sectional elevation of a pump body incorporating impeller vanes and means to provide a head of liquid for self priming.

FIG. 2 is an end sectional elevation of the embodiment illustrated in FIG. 1.

FIG. 3 is a longitudinal sectional elevation of a pump body wherein the impeller vanes project radially from the hub and impeller vane deflecting means is mounted in the outer wall of the pump chamber and functions also as an impeller seal between the outlet and inlet.

FIG. 4 is an end sectional elevation of the embodiment illustrated in FIG. 3.

FIG. 5 is a fragmentary sectional plan wherein the impeller vanes project laterally on each side of the impeller and the deflecting means are positioned to coact therewith.

FIG. 6 is a view similar to FIG. 5 wherein the impeller vanes are on one side of the impeller only.

FIG. 7 illustrates one form of means for actuating the deflecting means of FIG. 5.

Referring to FIGS. 1 and 2 this turbine pump comprises an internally cylindrical case 1 having an annular pump chamber 2 with an inlet port 3 and an outlet port 4 in the outer wall of the pump chamber both having means (not shown) for connecting to supply and delivery pipes.

In the outlet port 4 there is an air discharge liquid separation vessel 5. It is connected by port 6 to an ancillary reservoir 7 adjoining the pump chamber dimensioned to hold sufficient liquid to create a liquid seal within the pump chamber for a priming operation. Syphonic return flow is prevented by a bleed port 8.

A rotor drive shaft 9 extends axially into the case 1 through a gland l0 and a hub 11 on the shaft has an impeller l2 thereon. The impeller incorporates an array of vanes 13 made of an elastomeric material. There is a flow clearance between the vanes and all parts of the pump chamber except between the inlet and outlet ports where a working clearance only is provided.

In FIGS. 3 and 4 the vanes 13 project radially and have a degree of flexibility which will permit deflection between the inlet and outlet ports in a priming operation. A flexible plate 14 is secured to the peripheral wall of the pump chamber 2 between the inlet and outlet ports 3-4 as indicated at 15. It is adapted to be deflected by a spring retracted plunger 16 slidable in a hollow boss 17 on the pump case 1. There is a leak port 18 through the plate 14 and a complementary exhaust port 19 in the plunger 16 which is only open to the pump chamber and to atmosphere when the plunger is depressed as shown in FIG. 4.

In FIG. 5 the vanes 13a and 13b project laterally on each side of the impeller 12 and the pump chamber 2 is shaped to accommodate the vanes and to provide the flow clearance. Two flexible plates 14a and 14b are mounted on opposite side walls of the pump chamber 2 juxtaposed the inlet and outlet ports 3-4. They are adapted to be deflected by two spring retracted plungers 16a and 16b. Ports such as 18 and 19 are incorporated.

One means of depressing the plungers 16a and 16b in unison is illustrated in FIG. 7. The means comprise a U shaped member 20 pivotally mounted as at 21 on a bracket 22. The member 20 has its limbs 23 shaped to engage and depress the plungers 16a and 16b. It is provided with an operating handle 24.

In FIG. 6 the vanes project laterally only on one side of the impeller 12 and only one flexible plate and actuating plunger 16c is required.

In the embodiment described in FIGS. 1 and 2 the pump is self priming as long as the reservoir contains sufficient liquid to substantially immerse the vanes 13.

The partial circulatory effect of this liquid seal entrains, traps and ejects air drawn from the suction line until a pressure drop sufficient to induce flow from the connected source occurs.

Once normal flow is established the reserve reservoir is automatically replenished with liquid.

Pressure control is dependent on the type of elastomeric impeller vane employed. For low pressure duties where immediate cessation of flow is required without stopping the pump a more flexible impeller vane is used thereby allowing flow between the outlet and inlet ports by vane deflection due to back pressure. This means of internal by-pass of liquid dispenses with a mechanical by-pass.

In FIGS. 3 to 6 the working clearance between the impeller vanes and the walls of the pump chamber at the position, of the inlet and outlet ports is achieved by the flexible plates 14a, b and c. Other and/or supplementary means may be adopted or included. For example, the wall or walls of the pump chamber may have a projection or projections formed thereon having provision to accommodate vane deflecting means which in such a construction may be a spring retracted plunger or plungers of the type described but having a tapered nosing to contact the vanes.

In FIGS. 3 to 6 the pump is primed in a starting operation by deflecting the impeller vanes to substantially decrease the vane cell volume when passing between the outlet and inlet ports. The vane cell volume is restored to normal after passing the deflecting means thereby creating a suction efiect in juxtaposition to the inlet port. When pumping, fluid acceleration within the pump is created by a pressure differential generated between the walls of the pump chamber and the impeller vane cells. As the liquid velocity within the pump chamber is lower than within the impeller vane cells secondary and continually increasing circulation is induced. This progressive energy cycle escalates or regenerates" until the fluid is ejected through the outlet port. Regenerative pumps are advantageous for handling small fluid quantities against high operating head conditions. The shape and arrangement of the vanes and the cell capacity between them is determined according to work the pump is required to perform.

in F168. 3 to 6 means are incorporated such as a non return valve 25 to prevent back flow through the outlet port 4.

In all forms the flexible vane impeller allows for priming deflection if required and normal running without continuous running deflection when compared with the conventional continuous flexing impeller pump, thereby eliminating fatigue and ultimate failure as encountered with pumps as constructed hitherto.

The claims defining the invention are as follows:

1. A turbine pump comprising an internally cylindrical case having an annular pump chamber therein, an inlet and outlet port in the case communicating with g the pump chamber, a rotor drive shaft extending axially into the case, an air discharge liquid separation vessel in the outlet port and connected by a port to an ancillary reservoir connected to the pump chamber adapted to create a liquid seal in the pump chamber for a priming operation, an impeller on the drive shaft including flow vanes made of an elastomeric material, said pump chamber being dimensioned to provide a flow clearance between the flow vanes and all parts of the chamber except between the inlet and outlet where a working clearance only is provided, retractably means in the pump chamber between the inlet and outlet to deflect the vanes during a priming operation, said means comprising at least one flexible plate having a leak port and at least one spring retracted plunger also having a leak port, each said leak ports opening to the atmosphere when the plungers are depressed, said vanes returning to a normal non-deflected position when said plungers are restored to their non-depressed position once priming has been effected.

2. A turbine pump as claimed in claim 1 wherein the impeller is a disc and the flow vanes project radially from the impeller.

3. A turbine pump as claimed in claim 1 wherein the impeller is a disc and the flow vanes project laterally on each side of the impeller.

4. A turbine pump as claimed in claim 1 wherein the impeller is a disc and the flow vanes project laterally on one side of the impeller.

5. A turbine pump as claimed in claim 1 including means to prevent back flow through the outlet port.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION PATENT NO. 3 734, 638

DATED May 22, 1973 INVENTOR(S) Vivan Richard Ebsary It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown beiow:

(73) Assignee: None Signed and Sealed this eleventh D Of November 1 9 75 {SEAL} A nest:

RUTH-C. M AjSON C. MWRSHALL DANN .-i!!0srmg- ()[juer ('nmmissr'um'r 01' Pulenm uml Truilcmurkx 

1. A turbine pump comprising an internally cylindrical case having an annular pump chamber therein, an inlet and outlet port in the case communicating with the pump chamber, a rotor drive shaft extending axially into the case, an air discharge - liquid separation vessel in the outlet port and connected by a port to an ancillary reservoir connected to the pump chamber adapted to create a liquid seal in the pump chamber for a priming operation, an impeller on the drive shaft including flow vanes made of an elastomeric material, said pump chamber being dimensioned to provide a flow clearance between the flow vanes and all parts of the chamber except between the inlet and outlet where a working clearance only is provided, retractably means in the pump chamber between the inlet and outlet to deflect the vanes during a priming operation, said means comprising at least one flexible plate having a leak port and at least one spring retracted plunger also having a leak port, each said leak ports opening to the atmosphere when the plungers are depressed, said vanes returning to a normal non-deflected position when said plungers are restored to their non-depressed position once priming has been effected.
 2. A turbine pump as claimed in claim 1 wherein the impeller is a disc and the flow vanes project radially from the impeller.
 3. A turbine pump as claimed in claim 1 wherein the impeller is a disc and the flow vanes project laterally on each side of the impeller.
 4. A turbine pump as claimed in claim 1 wherein the impeller is a disc and the flow vanes project laterally on one side of the impeller.
 5. A turbine pump as claimed in claim 1 including means to prevent back flow through the outlet port. 